Control device for regulating flow of fluids in heat exchanging relation



y 1960 H. w. ANGELERY 2,946,508

CONTROL DEVICE FOR REGULATING FLOW 0F FLUIDS IN HEAT EXCHANGING RELATION Original Filed May 28. 1953 2 Sheets-Sheet 1 FIG. I.

INVENTOR. 44 4/ HENRY w. ANGELERY M.n.A-MWM his ,4 TTOEMFYS.

July 26, 1960 AN LERY 2,946,508

CONTROL. DEVICE FOR ULATING FLOW 0F FLUIDS IN HEAT EXCHANGING RELATION Original Filed May 28. 1955 2 Sheets-Sheet 2 4% /IIII/ l "m= M a W //0 23/ E /40 no.3 2;

INVENTOR. HENRY W. ANGELERY BY fl u,1.%,./MJWAM CONTROL DEVICE FOR 'REGULATING FLOW OF FLUIDS 'IN' HEAT EXCHAN GIN G RELATION Heury W: Angelery, 19 Gwynne .Court, Northvale,.N.J.

Original application-"May- 28,1953, Ser. No. 357,982,

now Patent No. 2,805,039, dated Sept. 3, 1957. Divided "and this application July 9, .1957, Ser. :No- 670,735

'Claims. 1 (Cl. 235-80) 357,982, filed May 28, l953,now Patent No. 2,805,039.

The term subject fluid asused herein is applied to the fluid whose final temperature and, if desired, state is to be controlled' The term regnant fluidas used herein is applied to the fluid used "to control the temperature or state, or both, of the-subject'fiuid. The flow of heat may be from the regnant fluid to the subject fluid or vice versa. Thu'syfor example, in a steam-water heat exchanger for maintaining the Water at a preselected tem perature, the steam is the'regnant fluid and the water is the subject fluid. In a refrigeration system, 'on'the other hand,*the refrigerating medium is the regnant fluid and the subject fluid may be air or some other fluid.

It is well known that the rate of heat transfer between twoifiuids'is 'a'function of their temperature differential and the eflective heating surface, i.e., the heat transfer area, in the heat exchanger. Therefore,to-maintainthe subject fluid .at a constant temperature with variations in heat demand, such "as those due to changes in rate of flow or incoming temperature of the subject fluid, the rate of heat transfer must be held in balance with the-'chang ing heat demands. If the heat transfer surface is assumed to remain constant, it becomes necessary to vary the temperature of the regnant fluid asthe heatdemand-changes, the variations in temperature of the regenant fluid being directly proportional'to .the changes in heat demand in order to maintain a balance between heat demande'd'and heat supplied.

The temperature of fluids in; the vaporstate; e.g., saturated steam,- is dependent on the pressure. The relation-of temperature to pressure is, however, byno means constant. Thus, for example, reference to the steam tableswillshowthatfor saturated steam, with a 5 lb. pressure difference from -15 to 20 p.s.i.a. (lbs. per square inch absolute), the temperature'difference is":l4.93 "R, from 65 to 70 p.s.i.a. it is 4.95 F., and from-115 to 120 p.s.i.a.: it is-or1ly 318 F. Hence, the 'tempera-ture-and pressure relation of saturated steam is a geometric-z or -exponentialfunction in which the exponent is -a value other than'one, as distinguished from a relation thatis constant and'can be termed a linear (orarithmetic) function; i.e., an exponential function; the exponent of which is one.-

It is apparent, therefore, that changing the pressureof the regnant fluid as a direct or linear function of changes in heat demand will not effect the proper balance inthe heat transfer rate and will not maintain the subject fluid at a constant temperature because of the aforementioned varyingrelation between temperature and pressure inthe. regnant .fluid. Also, a varying heat demand cannot be balanced properly by varying .the volume or quantity of flow of theregnant fluid Without control of its temperature or pressure; hence, the sensible temperature .of the 2,946,508 Patented July 26, 1960 2.. subject -fiuid, -e.g-., the outlet -:temperature :.-of. water-1;'in a steam-water: heat exchanger, :will not her-held constants under 'su'ch conditions;

In' control mechanisms known to have :beemproposed;

heretofore for regulating theiflo'w of steam in --response:

- to' a '-temperature*-sensitive device inthenwater or'other:

fluid to be'heated by the steam,-:proper considerationrhae not been given-to controlling this- -variable' relationsbeei tween the pressure and temperature i=of steameat low and highpres'sures" andits effect ou I the heat: transferrate Thus; for example, proposals: havebeen made .to provide: a thermostaucontrolled steam hvalve. which would openz whenever the sensible" or. actual temperature of the water; t'o-lbe heated -bythe steam fall's 2 below the preselected. or desired water? temperature and closes as soon as: the", sensible temperature of the-water reaches the preselected temperature. This does not 'take intoconsiderationa charge side- 0f 1 the valve in the heat exchangen varies d whether or inot-the-r-ateof ste'amflow into the heat ex; changer iwill be in -balance with the, rate of heat transfer required for the load or demand for heat. The degree to; which the I steam valve is opened in "mechanisms. of this type and," theref6re, the pressure "of the steamon the disa ready with the difference between 1 the preselected and the sensible temperatures of the water in the heat exehangenr This does not rovide the correlation 7 between :the dis-i charge ressure or. temperature =ofthe steam. and the temperature chan'ges 'in the water -that is 'necessary to' maintain the required balance between heat transfer rateand heat "demand -i'n thethea'ter. it' simply change's the volume or rate of flow of s'tea'mdir'ectly I with changes in the temperature of 'the wa'ten Beca s of this -ina'bilityof heretofore proposed mechanisms to maintain a properi balance tbetwee'ri heattransfer rate 5 and heat denian'd,= suchme'chanisms' tend 'to-hunt','i.e., go through-a cycle. of operations wherein the -sensible -water temperature alternately goes hi'gher and lower than desiredi When the fixed br a'rithmet ic' ratio of pressure change in steam to '-temperature chan in water'- is small in regulating' mechanisms #whi'ch vary the pressure of the 1 steam on the discharge side of the valve and :in the I heat exchangerdirectly with 2 the diife'r'e'nce' between i the we selected and' the sensible temp'erature of the water in a heat exchanger, thevaria'tions in=the sensible -temperatureof the water iitust be- -large"in'order to-signal -a large" demand -for'--heat -with' the result-that; the response of theme"ehanism 'to' a large demand forheat is sluggish; Cenverseiy; if f thefi aforementioned =fixed or arithmetic ratio is large,- such mechanisms hurlt-""When small de== mands for heat "are sen'se'dby relatively small changes in the sensible temper'ature' of the-water;

In order pro'perly toregula'te' the temperature of t-he subject fluid, the-temperature"regulator -must: be =-capable' of properly controlling'the heat input in 'di'reet' pro'portion to the changesin required heattrans-fer rate for the changeinheat deman'd as measured, for example' by wire rateof flow ""and incoming temperature of thesubject fluid! Sincethe h'ea't transfer: I rate --varie's' in direct proport-ion to'fchangesin the" temperature "-difil entifll be tween'th'e' subject and regna ntfluid's assuming-effectivehea'ting' surface remains c ons'tant, and the relati ori' be tween the temperature and the pressure of f'the regnarif fluid isvariable, i.e., a-geometric rather than anar-itlimetic -ratio, it isnecessary" to control the discharge-pres sure oftheregnant fluid'in a varying 'ratio to the chang s; in sensible temperature of the subject fluidf in orde'r}to mai-ntainthe heat 'transfer -'r-atein--balance'-with load changes (required heat input) of the subjeetffluids" time the'ratio is required'to be. relatively small whenthe sensible temperature of the subject fluid -approachesjthe" preselectedj temperature and. is' required to become,

progressively greater as the difference between the sensible and the preselected temperatures of the subject fluid increases.

A contributing factor in the inability of control mechanisms heretofore proposed to balance adequately the heat demand and the heat transfer rate'i's that great instability, often referred to as valve flutter, is encountered at some position or positions of the valve head in known pressure actuated main valves. This instability is due to variations in pressure differentials within the valve that are caused by the flow of fluid therethrough.

It is necessary for proper control of any function, whether it be that of temperature, pressure or any other function, that a pressure actuated main valve be instantly responsive, but with stability, to every impulse sensed and transmitted by its control mechanism. Also, it must be capable of closing tight under no flow conditions and of opening to maximum aperture required for maximum flow of regnant fluid without affecting its stability due to variations in pressure diiferential across the valve head or disk of the valve caused by variations in flow rate of the regnant fluid when modulating to any position.

The control mechanism of the present invention is unique in being responsive not only to any departure from the preselected temperature of the subject fluid and to the degree of departure therefrom, but is also capable of compensating for the variable relationship between the pressure and temperature of the regnant fluid in that it not only actuates a flow of the regnant fluid in relatively greater volume when the temperature differential is great and throttles said flow to a relatively smaller volumetric rate when the temperature differential becomes small, but also maintains the proper temperature and pressure relation of the regnant fluid to sensible ternperature of the subject fluid to maintain the heat transfer rate and the required demand for heat in proper balance. Also, the compensation for the variable relationship between the pressure and temperature of the regnant ,fluid is adjustable to maintain the proper heatbalance for fluids other than water and steam.

In the preferred embodiment of my invention, the control mechanism comprises a pressure actuated main valve, the actuating pressure of which is controlled by a differential pressure pilot which is operated primarily by a temperature actuated pilot response in variable degree to the temperature of the subject fluid. Means are provided for modifying the operation of the difierential pressure pilot by the pressure of the regnant fluid on the discharge side of the main valve. When the difference between the pressure at which the regnant fluid is available and the pressure of regnant fluid required to main-- tain the subject fluid at a preselected temperature is relatively small, the differential pressure pilot may be dispensed with and the main valve can be controlled directly by the temperature actuated pilot alone.

For optimum control of heat transfer between a regnant fluid and a subject fluid, I prefer to employ, in combination and close cooperation with the control mechanism of my invention, a novel pressure actuated main valve that is statically and dynamically balanced under all conditions of flow as a result of improvements not found in pressure operated main valves heretofore proposed. These improvements, which enhance significantly the sensitivity and stability of the main valve and cooperate with the control mechanism to maintain the desired, balance between heat demand and heat transfer rate, comprise a structure for reducing the force required initially to open the valve, stabilizing the pressure differential between the high and low pressure sides thereof when the valve is partly or completely open, and magnifying the displacement of the valve stem by the pressure diaphragm, thus reducing the displacement of the diaphragm and increasing its sensitivity to changes in pressure transmitted to it by the control mechanism.

The advantages and utility of the mechanism of this invention will become apparent from the following detailed description made with reference to the accompanying drawing, wherein:

Figure l is a sectional view in elevation of a preferred embodiment of the control mechanism and main valve of the invention taken on section line 1-1 of Figure 2;

Figure 2 is a plan view, with the cover removed, of the control mechanism shown in Figure 1;

Figure 3 is a sectional view in elevation, taken along section line 33 of Figure 2, of a portion of the control mechanism;

Figure 4 is a sectional view in elevation, taken along I section line 4-4 of Figure 2;

Figure 5 is an isometric view, partly cut away, showing a preferred construction of a lever forming an essential element in the control mechanism; and

Figure 6 is a plan view, similar to Figure 2, showing a modified form of the control mechanism.

Referring now to Figure 1 of the drawing, 10 represents a main valve having an inlet chamber 11 and a discharge chamber 12 connected to high pressure line 13 and low pres-sure line 14, respectively. The control mechanism for the main valve is indicated generally at 15 as being covered by a cover 16.

The main valve 10 is provided with a primary valve head 17, a primary valve seat 19, and a valve stem 20 riding in a stem guide bushing 21 and having a disk 22 biased by a spring 24 against a roller 26 on a lever 27. The lever 27 has a fulcrum at 29 and a pin 30 hearing against a diaphragm pressure plate 31 which in turn bears against a flexible diaphragm 3?. between upper and lower diaphragm chambers 34 and 36. a

The valve head 17 has an interior, secondary valve seat 37 and a shift 39 which is movable, as a unit with valve head 17, in a cylinder 40 held in position by main valve cap 41 and urged upward by a main spring 42 in a chamber 44 through the medium of a hollow boss 46. The upper portion or extension 47 of the valve head 17 is provided with vent ports 49 and accommodates a stern section 50 of reduced diameter carrying an interior, secondary valve head 51 urged upward against the interior valve seat 37 by a spring 52 seated on the boss 46, downward movement of the stem 2i relative to the valve head 17 being limited by abutment of a shoulder 54 against the upper portion 47 of the valve head. The inlet chamber 11 of the main valve is connected to a high pressure chamber 56 by means of a line 57 and the discharge chamber 12 communicates with the lower diaphragm chamber 36 by way of line 59.

The control mechanism i5 is mounted on the main valve 10 and generally includes a base 60, the lower portion 61 of which is secured to the main valve casing; a temperature actuated pilot 62, 64, shown best in Figure 1; and a differential pressure pilot 66, shown best in Figure 3.

The portion 62 of the temperature actuated pilot consists essentially of a thermostat bulb 67 installed at any with a decrease in said temperature.

desired location for sensing the actual or sensible temperature of the subject fluid (not shown). It is connected by means of a capillary tube 69 to a bellows 70 which, in turn, is secured to a plunger 71 movable vertically in the upper portion 72 of a telescoping housing 72, 74. The lower portion of the plunger 71 is in contact with a connecting piece '76 pivotally engaged with one arm 77a of a lever 77, the lower part of said connecting piece being engaged by a stem 79 guided for vertical movement on a stud 80 and biased upwardly by a spring 81. The bulb 67, tube 69 and bellows 70 form a closed chamber containing a fluid, preferably a liquid, which expands with an increase in temperature sensed by the bulb 67 and contracts The housing components 72, 74 are threaded at 82 for adjusting the pressure exerted against the bellows 70 by the springs 81 acting throughthestem179, theconnecting piece 76 and the plunger 71.

A shoe member 84 havingabearing surface 86 is attached to thehousing member 74 for vertical adjustment, as bymanipulation of a bolt 87 in a .fixed support 89, and for horizontal adiustment by selection of a spacer 90 of desired thickness and tightening .of a stud 91.. The bearing surface. 86 of the shoe member 84 may be of any desired shape that will insure movement of the point of contact of the bearing-surface with the lever 77, and therefore a translation, upon actuation of the lever, of the elfecfive-fulcrum along thelength thereof. As shown in Figure 1, for example, the bearing surface 86 may be convex so that upon clockwise rotation of the lever 77 the point of contact, i.e., the effective fulcrum, will moveto the left.

The lever 77, as shown best in Figure 5, comprises two telescoping members or arms 77a and 77b so that the horizontal distance between the connected extremities thereof. will remain constant upon tilting of the lever. The arm 77b, i.e., the left end of the lever as seen in Figure 1, is connected to,a stem 92 and a plunger 94 in portion 64 of-thetemperature actuated pilot by means of a connecting piece 96 similar in construction to connecting piece 76 andlil ewise pivotally engaged with lever 77. The stem 92, which may, if desired, be made of three separate but coacting parts, is movable vertically in stemguides 97 and 98, carries a valve head 99 at its lower end and is spring biased by spring 101) to resist downward movement.

The base 69 under the portion 64 of the temperature actuated pilot contains a first metering valve having an upper chamber 101 and a lower chamber 102'separated by a valve seat 104 for the valve head 99, leakage of pressure along the stem--9 2'being efiectivelysealed by a bellows-106 The lower-chamber 102 of the metering valve is connected to the high pressure chamber 56, and therefore by way of line 57 to the inlet chamber '11 of the mainvalve '10, by means of ports 107 in a boss 109 for the spring 100. The upper chamber 101 is connected, asshown best in Figures 2, 3 and 4, tothe difierential pressure pilot 66' byway of conduit 110 and linelll. A

pressnreequalizing assembly for the metering-valve 99 consists ofbellows 112secured to the plunger 94 and connected to the highpressure chamber 56 by way of line 114..

The differential pressure pilot 66, shown bestin Figure 3,'- in essence comprises a housing 116 containing bellows 117; 119 and 120 and the upper portionof a valvestem 121 movable vertically .in stem guides122 and 124, and a second metering valve having an upper chamber-126a lower chamber 127, and :a valve seat 129 for a valve head I30 carried ,onthelowerend of; the stem 121 may, like stem 92, be madeof three separate parts if desired. 7 The housing-116 is secured in position above the base 60 by anurnber of tie rods 131. A first chamber 132 formed by thehousing-116 and bellows 117 and. 119 is connected tothe upper chamber 101 of thefirst metering valve by wayof linev 111 and conduit 110 and tothe low pressure line 14 connectedto the dischargechamber 12 of the main valve by way of line 111, conduit 110, line 133 provided with a fixed orifice 134, chamber 135 and line 136. A second chamber 139 formedby housing 116 and bellows 119 and 120 is connected tothe low pressure line 14 by way of line 140, chamber 135 and line 136. The stem 121 is spring biased to resist downward movement by springs 141 and 142' and regulation of the spring loading .on the stem is effected by adjustment of a nut 144 on which the spring 141 is seated. Leakage of pressure from upper chamber 126 along the stem 121 is eifectively sealed by bellows 146.

The upper chamber 126 of the second metering valve communicates with the upper diaphragm chamber- 34 of the main valve 10 by way of conduits 147 and 149 and withthe low pressure line 14 by way of conduit 147, line Ell-provided with a fixedorifice 151,. chamber 135 and line liid The lower chamber 127 is connected. to

the high pressuregchamber 56nby means. of ports. 15-2 in a boss154forthe spring 142.v

In operation,the metering valve 99 between chambers 101 and l02 and valve 130 between chambers 126, 127 are normally.- maintained in closed positions by, springs and 141, 142, respectively. The metering valve 99; of the temperature: actuated pilot 62,. 64 .is opened when the thermostat 6'7 senses a departure from thepreselected temperaturethe subject fluid. Opening-ofithe metering valve 99in turn actuates the second metering valve'130 through themedium of pressure in the chamber 132 exerted bythe regnant -fluid inhigh pressure chamber 56, by way of metering valve-9,9, conduit 111! and line111. Upon opening of the second'meteringvalve 130, pressure is transmitted through the valve from chamber'56 through ports 152 and lower chamber127 to the upper diaphragm chamber 340i the valve 10 by; way; of conduits 1-47 and 149.

Thus, for example, when the inlet chamber .11qis connected to. a source of high pressure steam and the thermostat bulb 67 is immersed in-water that is in heat exchange relation with steam from the discharge chamber- 12.. a lowering of the'sensible temperature of thewater, i.e., a demand for heat, is reflected by a contraction -of the bellows 7t) and consequently by an upward movement of the plunger 71; This in turn operates to rock therlever 77 in a'counterclockwise direction and causes the stem 92tobe depressed, thus opening the first metering valve 99 against the action 'ofspring 100; Upon counterclockwise rotation of the lever 77, the eifective fulcrum, for the lever moves toward therightend thereof, as seen in Figure ,1, thus-varying the ratio of the lengthyof the-lever arm actuated by the combined action of the ,plungerfll, the stern -79jan d the spring 81 to the length of the'lever ar1:o --ai :t-ir tg on; the stem 92;, Because-of the movement of the, elfective fulcrum, point for the lever 77,- the degree to which the metering valve 99 is opened is a variable (geometric); function of the diiferencebetween the sensible temperature of the water and the preselected temperature As the first metering-valve 99 is opened, pressure {:18 exerted in chamber 132 of the difierential pressure pilot 66 to depress the stem 121 and open the second; metering valve 130. The fixed orifice 134 in line 133'acts to permit thegradual build-up of pressureinchamber 132 as; the

metering valve 99 of the temperature actuated pilot is opened. The pressurein chamber 1321s further; compensated impart by a pressure in chamber 1393Whl0h18 substantially equalto thepressure in, the ,low pressure line 14- connected to the discharge chamber: 12 ,of {the main valve anclin part by-the springs 141 and 142.: As the-metering'valve opens, direct; cornmunic'ation is provided between the-high pressure side of the main valve 10 and the upper diaphragm chamber 34 of the valves-10 by way of line 57, high pressure chamber, 56, valve 130,

and conduits 147 and 149. The pressure thus transmitted to the 1 Pperdiaphragm-chamber 34 depressesthe flexible diahragmj32 and therefore also diaphragm pressure plate 31. The downward movement of the pressure plate: is magnifiedand transmitted to the disk 22 and the valve stem-20, due to the ratio of movementarms on theilever 27, against; the'upwardthrust of springs -24,v 42,and-:52 and the unbalanced differential pressure across rrmain valve head ;17f andinterior valve head 51. The initial downward movement of valve stem 29 depresses stemsection; 50 and forces the interior valve head 51'to= leave itsvsea-t, 37- against the force of spring 52 and the unbalanced pressureagainst the valve head 51. This opening of the interior valve permits the accumulation of steam caused by leakage between skirt 339 and cylinder 40 in thechamber 44 to be vented or discharged torthe low-:pressureline 14, thereby atrleast partially equalizing the pressure across the main valve head 17; Further downward movement of stem 20 results in. contact betweemthe shoulder 54 andthe upper portionr'47 'of the spring 42 to permit direct flow of steam from high pressure chamber 11 to low pressure chamber 12 of the main valve and then to a heat exchanger, not shown.

The flow of steam between the valve head 17 and valve seat 19 is accompanied by a local lowering of static pressure, due to the Venturi etlect produced by the flow into the wider space between the extension 47 and the sleeve 19.and generally clockwise across the concavelycurved surface at the junction of the extension and with the valve head 17, and aspirates the steam from chamber 44 through the vent ports 49, thereby equalizing the static pressure on the valve head 17 despite variations in the flow rate of steam between the valve head 17 and valve seat 19. Flow of steam through the ports 49 equalizes the pressures on opposite sides of the valve and since the pressure is always balanced across the main valve head 17 under any condition of flow through the valve, the force of the loading pressure against flexible diaphragm 32 is always strictly balanced against only the forces of springs 24 and 42, thereby eliminating the pulsation or fluttering of the valve head ordinarily encountered in heretofore proposed designs of pressure actuated main valves because of unbalanced pressure forces which constantly vary with changes in flow rate of steam. The orifice 151 in line 150 permits the gradual increase of pressure in upper diaphragm chamber 3 1 as the valve 130 of differential pressure pilot 66 is being opened by the loading pressure from the temperature actuated pilot 62, 64. The lever and pressure plate assembly 26-31 increases the sensitivity of the main valve to changes in pressure differential in upper and lower diaphragm chambers 34 and 36 and etfectively reduces the amount of movement required for diaphragm 32.

As the pressure of the steam in the low pressure line 14 builds up, it is transmitted by way of line 136, chamber 135 and line 1413 to the chamber 139 formed by the bellows 119 and 120. This pressure thereforetends to counteract the pressure in chamber 132 and to effect a throttling of the metering valve 130 and consequently also a throttling of the main valve 10 due to a decrease in pressure on the diaphragm 32. When the thermostat 67 is satisfied, i.e., when the temperature of the water has reached the-preselected temperature, the fluid in the thermostat bulb 67, capillary tube 69 and bellows 70 will have expanded to an extent sufiicient to depress the plunger 71 and raise the stem 92 to such an extent that the metering valve 99 will have been closed. This cuts off the pressure in the chamber 132 of the differential pressure pilot 66 and thereby operates to close metering valve 130 as well, with the result that the pressure on the diaphragm 32 of the main valve 10 will be reduced to a degree sufiicient to close it.

In closing, the main valve head 17 contacts the main valve seat 19 in a completely balanced condition with respect to varying pressures caused by changes in steam flow. Further upward movement of main valve stem 20 allows the interior valve head 51 to be seated on the seat 37, closing the main valve 10 completely. Steam from the high pressure side 11 of the valve thereupon leaks between the skirt 39 and the cylinder 40 to accumulate in chamber 44 and creates a pressure differential across the main valve head '17. This differential in pressure assists main spring 42 and spring 24 in maintaining a positive closing of the main valve 10 under no flow conditions.

Because of the variable fulcrum for the lever 77, the opening of the metering valve 99 in the temperature actuated pilot 62, 64 and therefore also the opening of the metering valve 130 in the differential pressure pilot 66 is controlled by the difierence between the preselected water temperature and the actual or sensible temperature thereof as sensed by thermostat 67. If the difference is great, the counterclockwise rotation of the lever 77 is correspondingly great and the downward movement of the stem 92, and therefore of the metering valve head 99, will be a multiple of the upward movement of the plunger 71 and bellows 76 for the reason that under such conditions the point of contact between the lever 77 and the shoe member 84 will be relatively close to the end of the lever actuated by the plunger 71. As the lever 77 becomes more nearly level due to the approach of the sensible temperature to the preselected temperature, the point of contact moves to the left, as seen in Figure 1, with the consequence that the vertical movement of the plunger 71. It is apparent, therefore, that the degree to which the metering valve 99 is opened due to actuation by the thermostat is a geometric rather than a linear function of the difference between the sensible temperature sensed by the thermostat and the preselected temperature for which the mechanism has been set by adjustment of the vertical and horizontal position of the shoe member 84, as well as by the curvature and length of the bearing surface 86. The fixed orifices 151 and 134 are designed to meter properly the flow of high pressure steam which flows throuugh the dillerential pressure actuated pilot 66 and temperature actuated pilot 62, 64, respectively, in order to build up gradually the operating pressure to main valve diaphragm 32 and the loading pressure to the differential bellows chamber 132 of the dilierential pressure actuated pilot 66. Conversely, when the respective pilots operate to reduce the pressures in conduits 147, 149, 159 and 110, 111, the fixed orifices 151 and 134 act as vents to permit the residual pressures to be vented from the respective upper metering valve chambers 126 and 101.

The pressure equalizing bellows 112 for the metering valve 99 reduces the force required by spring 81 to elevate plunger 71, move lever 77 counterclockwise, and open the temperature actuated metering valve 99, when high pressure steam enters the inlet chamber 11 of the main valve 10. This partial balancing of the force of spring 81'not only increases the sensitivity of the metering valve 99 to small changes in temperature sensed by the thermostat 67 but permits the bellows 7G to expand and thus avoids rupture of the thermal system in the event the temperature sensed by the thermostat should for some reason exceed appreciably the preselected temperature.

A typical embodiment of the invention in which the differential pressure pilot 66 and pressure equalizing bellows 112 are omitted is illustrated in Figure 6 of the drawing. In this instance, the upper chamber 101 of the temperature actuated pilot 62, 64 is connected directly to the upper diaphragm chamber 34 of the valve 10 by way of conduit 111), line 156 and conduit 149 and to the low pressure line 14 by way of conduit 119, line 133, fixed orifice 134, chamber and line 136.

The operation of this embodiment of the invention is substantially similar, in so far as the temperature actuated pilot is concerned, to the operation described with reference to Figure 1. The only important diiference is that the pressure in the upper chamber 101 of the metering valve is transmitted directly to the upper diaphragm chamber 34 of the valve 19 and that the amount of pressure so transmitted to the upper diaphragm chamher is metered and controlled by the relation between the variable opening of the metering valve 99 and the fixed orifice 134 in the line 133 which communicates with the low pressure line 14. When low pressure steam enters the main valve 10, and the degree of control of the outlet temperature of the steam is not extremely critical, the modulation of the operating pressure transmitted to the upper diaphragm chamber 34 of the pressure actuatedmain valve 10. can be satisfactorily. accomplished by the variable metering of the temperature actuated pilot 62, 64, with the varying fulcrum lever action and the relation between the fixed orifice 134 and the variable opening of the valve 99.

Numerous modifications and applications will immediately become apparent to those skilled in the art on reading this description. It is to be understood that all such modifications and applications are intended to be included within the scope of the invention as defined in the accompanying claims.

I claim:

1. In a control device for regulating the delivery of a regnant fluid for heat exchange with a subject fluid to maintain said subject fluid at a preselected temperature, said device comprising a main valve for the regnant fluid, a temperature actuated pilot including a thermostat sensitive to the sensible temperature of the subject fluid and a differential pressure pilot actuated by the temperature actuated pilot and sensitive to a pressure differential of the regnant fluid in advance of and behind the main valve, said differential pressure pilot being interposed between the temperature actuated pilot and the main valve for actuating the main valve, the improvement which comprises means in the temperature actuated pilot responsive to the thermostat for actuating the differential pressure pilot when the sensible temperature of the subject fluid departs from said preselected temperature, the degree to which the thermostat responsive means actuates the pressure pilot being a variable function of the degree of departure of the sensible temperature from said preselected temperature and the degree to which the diflerential pressure pilot opens the main valve being a pressure compensated variable function of said degree of departure.

2. In a control device for regulating the delivery of a regnant fluid for heat exchange with a subject fluid to maintain said subject fluid at a preselected temperature, said device comprising a main valve for the regnant fluid, a temperature actuated pilot including a thermostat sensitive to the sensible temperature of the subject fluid and a differential pressure pilot actuated by the temperature actuated pilot and sensitive to a pressure differential of the regnant fluid in advance of and behind the main valve, said diflerential pressure pilot being interposed between the temperature actuated pilot and the main valve for actuating the main valve, the improvements which comprise means in the temperature actuated pilot responsive to the thermostat for actuating the differential pressure pilot when the sensible temperature of the subject fluid departs from said preselected temperature, the degree to which the thermostat responsive means actuates the pressure pilot being a variable function of the degree of departure of the sensible temperature from said preselected temperature and the degree to which the difierential pressure pilot opens the main valve being a pressure compensated variable function of said degree of departure, and means in the temperature actuated pilot responsive to the pressure of the regnant fluid in advance of the main valve for cooperating with the thermostat in the actuation of the differential pressure pilot.

3. In a control device for regulating the delivery of a regnant fluid for heat exchange with a subject fluid to maintain said subject fluid at a preselected temperature, said device comprising a main valve for the regnant fluid, a temperature actuated pilot including a thermostat sensitive to the sensible temperature of the subject fluid and a diflerential pressure pilot actuated by the temperature actuated pilot and sensitive to a pressure difl'erential of the regnant fluid in advance of and behind the main valve, said diiferential pressure pilot being interposed between the temperature actuated pilot and the main valve for actuating the main valve, the improvements which comprise first and second pressure chambers and a metering valve in the differential pressure pilot, said first pressure chamber actuating the metering valve and communicating with the regnant fluid in advance of the main valve under control of the temperature actuated pilot and with the regnant fluid behind the main valve through a line provided with a restricted orifice, and said second pressure chamber counteracting the actuation of the metering valve by the first chamber and communicating without substantial restriction with the regnant fluid behind the main valve.

4. 'In a control device for regulating the delivery of a regnant fluid for heat exchange with a subject fluid to maintain said subject fluid at a preselected temperature, said device comprising a main valve for the regnant fluid, a temperature actuated pilot including a thermostat sensitive to the sensible temperature of the subject fluid and a difierential pressure pilot actuated by the temperature actuated pilot and sensitive to a pressure difierential of the regnant fluid in advance of and behind the main valve, said differential pressure pilot being interposed between the temperature actuated pilot and the main valve for actuating the main valve, the improvement which comprises means in the main valve for increasing its sensitivity to actuating pressure transmitted to it from the diflerential pressure pilot, said means including a flexible diaphragm responsive to said actuating pressure, a valve stem, means for transmitting and magnifying movement of the diaphragm to the stem, a secondary valve head unseatable from a secondary valve seat upon a small initial increment of movement of the stern for venting regnant fluid through the valve, and a primary valve head unseatable from a primary valve seat by a further and more substantial movement of the stem.

5. A control device for regulating the delivery of a regnant fluid for heat exchange with a subject fluid for maintaining the subject fluid at a preselected temperature which comprises a main valve for the regnant fluid; a temperature actuated pilot including a thermostat sensitive to the sensible temperature of the subject fluid, a metering valve for actuating the main valve, and means interposed between the thermostat and the metering valve for opening the metering valve when the sensible temperature departs from the preselected temperature, the degree to which said interposed means opens the metering valve being a variable function of the degree of departure of the sensible temperature from the preselected temperature; and a diiferential pressure pilot actuated by the temperature actuated pilot and sensitive to a pressure differential of the regnant fluid in advance of and behind the main valve, said differential pressure pilot being interposed between the temperature actuated pilot and the main valve for actuating the main valve in response to a demand for regnant fluid sensed by the thermostat and in response to the pressure difierential; whereby the delivery of regnant fluid through the main valve is a variable function of the degree of departure of the sensible temperature from the preselected temperature compensated by the pressure differential.

References Cited in the file of this patent UNITED STATES PATENTS 555,738 Rushton Mar. 3, 1896 1,247,216 Brown Nov. 20, 1917 1,556,639 Sheer Oct. 13, 1925 2,035,166 Kimball Mar. 24, 1936 2,040,109 Spence May 12, 1936 2,388,457 Ziegler Nov. 6, 1945 2,401,144 Dube May 28, 1946 2,536,184 Johnson Jan. 2, 1951 2,589,251 Heinz Mar. 18, 1952 2,679,829 Gorrie et al June 1, 1954 OTHER REFERENCES McRae: Pages 399, 400 and 436 of Instruments" magazine, July 1943.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent N00 2 946,508 July 26 1960 Henry We Angelery It is herebfi certified that error appears in the-printed specification of the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

Column 8, line 14 after "movement" insert of the stem 92 may become equal to or even smaller than the vertical movement Signed and sealed this 10th day of January 1961.,

(SEAL) Attest:

KARL Hg AXLINE ROBERT C. WATSON Commissioner of Patents Attesting Officer 

